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In structural mechanics, the equations relating stress and strain arise from the balance of forces in the material medium. Plane stress is a condition that prevails in a flat plate in the x-y plane, loaded only in its own plane and without z-direction restraint.
The stress-strain relation can then be written, assuming isotropic and isothermal conditions
$$\left(\begin{array}{c}{\sigma}_{x}\\ {\sigma}_{y}\\ {\tau}_{xy}\end{array}\right)=\frac{E}{1-{\nu}^{2}}\left(\begin{array}{ccc}1& \nu & 0\\ \nu & 1& 0\\ 0& 0& \frac{1-\nu}{2}\end{array}\right)\left(\begin{array}{c}{\epsilon}_{x}\\ {\epsilon}_{y}\\ {\gamma}_{xy}\end{array}\right),$$
where σ_{x} and σ_{y} are the normal stresses in the x and y directions, and τ_{xy} is the shear stress. The material properties are expressed as a combination of E, the elastic modulus or Young's modulus, and ν, Poisson's ratio.
The deformation of the material is described by the displacements in the x and y directions, u and v, from which the strains are defined as
$$\begin{array}{c}{\epsilon}_{x}=\frac{\partial u}{\partial x}\\ {\epsilon}_{y}=\frac{\partial v}{\partial y}\\ {\gamma}_{xy}=\frac{\partial u}{\partial y}+\frac{\partial v}{\partial x}.\end{array}$$
The balance of force equations are
$$\begin{array}{c}-\frac{\partial {\sigma}_{x}}{\partial x}-\frac{\partial {\tau}_{xy}}{\partial y}={K}_{x}\\ -\frac{\partial {\tau}_{xy}}{\partial x}-\frac{\partial {\sigma}_{y}}{\partial y}={K}_{y},\end{array}$$
where K_{x} and K_{y} are volume forces (body forces).
Combining the preceding relations, we arrive at the displacement equations, which can be written
$$-\nabla \xb7\left(c\otimes \nabla u\right)=k,$$
where c is a rank four tensor (see c for Systems), which can be written as four 2-by-2 matrices c_{11}, c_{12}, c_{21}, and c_{22}:
$$\begin{array}{c}{c}_{11}=\left(\begin{array}{cc}2G+\mu & 0\\ 0& G\end{array}\right)\\ {c}_{12}=\left(\begin{array}{cc}0& \mu \\ G& 0\end{array}\right)\\ {c}_{21}=\left(\begin{array}{cc}0& G\\ \mu & 0\end{array}\right)\\ {c}_{22}=\left(\begin{array}{cc}G& 0\\ 0& 2G+\mu \end{array}\right),\end{array}$$
where G, the shear modulus, is defined by
$$G=\frac{E}{2\left(1+\nu \right)},$$
and µ in turn is defined by
$$\begin{array}{l}\mu =2G\frac{\nu}{1-\nu}.\\ k=\left(\begin{array}{l}{K}_{x}\\ {K}_{y}\end{array}\right)\end{array}$$
are volume forces.
This is an elliptic PDE of system type (u is two-dimensional), but you need only to set the application mode to Structural Mechanics, Plane Stress and then enter the material-dependent parameters E and ν and the volume forces k into the PDE Specification dialog box.
In this mode, you can also solve the eigenvalue problem, which is described by
$$\begin{array}{c}-\nabla \cdot (c\otimes \nabla u)=\lambda du\\ d=\left(\begin{array}{cc}\rho & 0\\ 0& \rho \end{array}\right).\end{array}$$
ρ, the density, can also be entered using the PDE Specification dialog box.
In the Plot Selection dialog box, the x- and y-displacements, u and v, and the absolute value of the displacement vector (u, v) can be visualized using color, contour lines, or z-height, and the displacement vector field (u, v) can be plotted using arrows or a deformed mesh. In addition, for visualization using color, contour lines, or height, you can choose from 15 scalar tensor expressions:
$${u}_{x}=\frac{\partial u}{\partial x}$$
$${u}_{y}=\frac{\partial u}{\partial y}$$
$${v}_{x}=\frac{\partial v}{\partial x}$$
$${v}_{y}=\frac{\partial v}{\partial y}$$
exx, the x-direction strain (ε_{x})
eyy, the y-direction strain (ε_{y})
exy, the shear strain (γ_{xy})
sxx, the x-direction stress (σ_{x})
syy, the y-direction stress (σ_{y})
sxy, the shear stress (τ_{xy})
e1, the first principal strain (ε_{1})
e2, the second principal strain (ε_{2})
s1, the first principal stress (σ_{1})
s2, the second principal stress (σ_{2})
von Mises, the von Mises effective stress
$$\sqrt{{\sigma}_{1}^{2}+{\sigma}_{2}^{2}-{\sigma}_{1}{\sigma}_{2}}.$$
For a more detailed discussion on the theory of stress-strain relations and applications of FEM to problems in structural mechanics, see Cook, Robert D., David S. Malkus, and Michael E. Plesha, Concepts and Applications of Finite Element Analysis, 3rd edition, John Wiley & Sons, New York, 1989.
Consider a steel plate that is clamped along a right-angle inset at the lower-left corner, and pulled along a rounded cut at the upper-right corner. All other sides are free.
The steel plate has the following properties: Dimension: 1-by-1 meters; thickness 1 mm; inset is 1/3-by-1/3 meters. The rounded cut runs from (2/3, 1) to (1, 2/3). Young's modulus: 196 · 10^{3} (MN/m^{2}), Poisson's ratio: 0.31.
The curved boundary is subjected to an outward normal load of 500 N/m. We need to specify a surface traction; we therefore divide by the thickness 1 mm, thus the surface tractions should be set to 0.5 MN/m^{2}. We will use the force unit MN in this example.
We want to compute a number of interesting quantities, such as the x- and y-direction strains and stresses, the shear stress, and the von Mises effective stress.
Using the PDE app, set the application mode to Structural Mechanics, Plane Stress.
The CSG model can be made very quickly by drawing a polygon with corners in x = [0 2/3 1 1 1/3 1/3 0] and y = [1 1 2/3 0 0 1/3 1/3] and a circle with center in x = 2/3, y = 2/3 and radius 1/3.
The polygon is normally labeled P1 and the circle C1, and the CSG model of the steel plate is simply P1+C1.
Next, select Boundary Mode to specify the boundary conditions. First, remove all subdomain borders by selecting Remove All Subdomain Borders from the Boundary menu. The two boundaries at the inset in the lower left are clamped, i.e., Dirichlet conditions with zero displacements. The rounded cut is subject to a Neumann condition with q = 0 and g1 = 0.5*nx, g2 = 0.5*ny. The remaining boundaries are free (no normal stress), that is, a Neumann condition with q = 0 and g = 0.
The next step is to open the PDE Specification dialog box and enter the PDE parameters.
The E and ν (nu) parameters are Young's modulus and Poisson's ratio, respectively. There are no volume forces, so Kx and Ky are zero. ρ (rho) is not used in this mode. The material is homogeneous, so the same E and [[ν apply to the whole 2-D domain.
Initialize the mesh by clicking the Δ button. If you want, you can refine the mesh by clicking the Refine button.
The problem can now be solved by clicking the = button.
A number of different strain and stress properties can be visualized, such as the displacements u and v, the x- and y-direction strains and stresses, the shear stress, the von Mises effective stress, and the principal stresses and strains. All these properties can be selected from pop-up menus in the Plot Selection dialog box. A combination of scalar and vector properties can be plotted simultaneously by selecting different properties to be represented by color, height, vector field arrows, and displacements in a 3-D plot.
Select to plot the von Mises effective stress using color and the displacement vector field (u,v) using a deformed mesh. Select the Color and Deformed mesh plot types. To plot the von Mises effective stress, select von Mises from the pop-up menu in the Color row.
In areas where the gradient of the solution (the stress) is large, you need to refine the mesh to increase the accuracy of the solution. Select Parameters from the Solve menu and select the Adaptive mode check box. You can use the default options for adaptation, which are the Worst triangles triangle selection method with the Worst triangle fraction set to 0.5. Now solve the plane stress problem again. Select the Show Mesh option in the Plot Selection dialog box to see how the mesh is refined in areas where the stress is large.
Visualization of the von Mises Effective Stress and the Displacements Using Deformed Mesh